Multi-bank radial type machine



Nov. 24, 1964 o. F. A BI'GlNELLl MULTI-BANK RADIAL TYPE MACHINE FiledSept 9, 1960 2 Sheets-Sheet 1 l P2 P3 P4 PI P3 R2 35 F F FF 50 54 33 1FF 50 1 h LJ F F u b b b 0 R2 0] b b b c 39 FIG. 6

Nov. 24, 1964 o. F. A. BIGINELLI MULTI-BANK RADIAL TYPE MACHINE 2Sheets-Sheet 2 Filed Sept. 9, 1960 United States Patent 3,153,935MUL'il-EANK FiAl'llAL TYPE MACHEQE Ureste Fiavio Alfredo Biglnelli, 22Rare do Marechal Foch, @ierrnonhFerrand, France Filed Sept. 9, 196i),Ser. No. 55,041 priority, application France, Nov. 26, 195$,

8ll,342, Patent 1,241,097 2 Claims. (Cl. 74-459) Piston machines arealready known, in which the pistons are actuated by an eccentric mountedon the shaft, the rotation movement of this shaft causing the rise andfall of the pistons by rotation of the eccentric.

In the case where the machine drives, the thrust of the pistons causedby the driving fiuid effects the rotation of the shaft by acting on theeccentric.

in these known machines such as pumps, the shaft is generally formed asa crankshaft, and comprises a cylindrical part off-centered in relationto the rotation axis. Roller bearings are mounted on this off-centeredpart. Their external cages control the clearance in the radial directionof the pistons of the pump.

in pumps of this type with a considerable delivery, We are obliged toarrange the cylinders and pistons radially in several planes parallelbanks perpendicular to the axis of the shaft. The single eccentricdevice then has the disadvantage that the pistons on one side of theshaft, at the moment of the compression stage, have a component actionof the same radial direction on the shaft, the pistons on the other sideare at the intake stage and have a zero component action on the shaft.Thus, the bearings receive the whole of the load due to half thepistons.

The present invention has more particularly the object of effecting animproved arrangement of the pistons and shaft of a multi-cylinder bank,radial type piston machine, the pistons of the various cylinder banksbeing placed in opposition so that the reaction forces of the pistonsand shaft divide up into two groups of equal power, but opposed.

The invention enables the reduction, to a great extent, of the reactionsupport of the shaft by these bearings, and hence, to ensure longer andmore efficient service of the bearings, particularly in the case ofintensive use.

The invention possesses the advantage of being adaptable to any radialtype of multiple bank piston machine. The invention especially relatesto a machine in which a simple and etlicient means of effecting thearrangement comprises roller bearings or ball bearings with anoff-centered bore slipping on to the shaft with which they arerotatively integral, this arrangement affording an easy and speedyassembly of the. machine.

Another advantage of the invention is the rotational integralization ofthe bearings and shaft ensured by longitudinal fiutings or grooves ofthe shaft cooperating with complementary fiutings provided in theoil-centered internal rin of the bearings, enabling each bearing playingthe part of eccentric to be fitted with any kind of orientation, withoutcausing any difficulty in fitting. The grooves extend axially along aportion of a drive shaft and the bearin s having an inner bore withprojections extending radially inwardly for driving the bearings fromthe shaft. Moreover, the bearings can be slipped on or off the shaft atone end as described hereinafter.

The arrangement and the radial type multi-cylinder bank piston machineor" the invention are shown, by way of example, in the particularapplication to a pump in the attached drawings, in which:

FIGURE 1 is a diagram showing the arrangement of the forces acting onthe shaft and the reactions of support of the shaft in its bearings inthe case of a single-eccentric pump.

3,15%,h35 Patented Nov. 24, 1964 FIGURES 2 and 3 show the arrangement ofthe forces acting on the shaft and the reactions of support of the shaftin its bearings according to two examples of application of theinvention.

FIGURE 4 shows, in axial section, a pump in which the invention isincorporated.

FIGURE 5 shows a sectional elevation of the shaft and the arrangement ofpistons around the eccentric.

FIGURE 6 shows an embodiment of the piston md its drive on theeccentric.

In the known single-eccentric pumps, we have stated that the bearingsreceive the whole of the load due to half of the pistons in theircylinders. In this case, the shaft St) is subected in the hypothesis ofpistons of four cylinder banks to forces F separated by a distance [2corresponding to the distance between the cylinder banks P P P P Thereactions of support of the shaft 56 on the bearings 33 and 34 arerepsectively shown by the arrows R and R the distance between thebearing 33 and the force F of pistons of the first cylinder bank isdenoted by a; the distance between the bearing 34 and the force F ofpistons of the last cylinder bank is denoted by C. The total distancebetween the bearings 33 and 34 is denoted by L.

In these conditions, the computation of the reactions on the bearingsgives:

We see that the reactions on the bearings are very considerable.

To obviate this disadvantage, according to the invention, an individualeccentric is used for each cylinder bank for putting the pistons of onecylinder bank, for example, successively in opposition to the pistons ofthe other cylinder bank.

In these conditions, FIGURE 2 shows the arrangement of the forces actingon the shaft 5t? and the reactions of support of the shaft in itsbearings 33 and 34.

The forces F acting on the shaft 50 of these the pistonsof cylinders Pand P are in opposition with the forces F acting on the shaft 50 due tothe pistons of cylinder banks P and P 1 In these conditions, thecomputations of the reactions R' and R on the bearings 33 and 34 give:

By considering that the value of the distance between the centers 0 andc is generally greater than that of the distance b, we see that thereactions R have values at the most equal to of the reactions R and R(the case of FIGURE 1).

It is also easy to see that the device according to diagram 1 involves agreater force exerted on the shaft to deflect it than in the deviceaccording to diagram 2.

Obviously, we can modify the arrangement of FIG. 2 without going outsideof the scope of the invention for this purpose, by opposing the forcesin pairs acting on the shaft into a multi-eccentric crankshaft reveals afitting.

ditliculty if it is required to retain the simple device of rollerbearings as intermediary for the transmission of the eccentric movementto the pistons.

The machine according to the invention eliminates the above-mentioneddifiiculty by effecting an arrangement of the shaft and removable rollerbearings controlling the pistons which enables various orientations ofthe eccentrics to be obtained from one cylinder bank to another, bymeans of a possible and easy fitting.

The principle of this device is as follows:

The shaft 54) of the machine does not comprise any eccentric, but acylindrical part with longitudinal fiutings. The various roller bearingscorresponding to each cylinder bank are fitted on to this part of theshaft. These bearings have an internal ring whose bore is off-centeredand machined into complementary shapes for engaging the flutings on theshaft. The internal ring is thus keyed on to the shaft and in therotation movement of the shaft acts as an eccentric. Each bearing canthus be fitted with any kind of orientation of the eccentric, withoutany fitting difiiculty arising therefrom.

In the machine, such as the pump shown in FIGURE 4, the pistons arearranged in four cylinder banks marked P P P P in accordance with thestructure of FIGURE 2.

In each cylinder banks, eight cylinders and thin pistons are arrangedradially around the shaft 50 spaced 45 from each other.

The pump is formed by a special cast-iron body 1 of general cylindricalshape with horizontal axis mounted on a stand 2, to which it is attachedby bolts 3. The body is bored successively along its axis at 4 forreceiving the side plate 5 supporting the bearing on the drive side, at6 for housing eccentrics fitted on the shaft 50 and at 7 for receivingthe roller bearing on the opposite side to the drive. A screw plug 8closes the end of the bore and is provided for facilitating disassembly.Two circular channels 9 and 10 are respectively reserved in the body ateach end of the cylinder. The channel 9 acts as intake collector. Theinlet nozzle 11 connected with the supply tank emerges in thiscollector. The channel 10 acts as delivery collector. The outlet nozzle12 emerges in this collector. The four cylinder banks P P P P normal tothe axis, are each formed by eight radial borings, such as 13, atangular intervals of 45 This radial arrangement coincides in thecylinder banks P P on the one hand, and in the cylinder banks P R, onthe other.

For smoother running of the machine the pairs of cylinder banks can bestaggered for n being the number of cylinders, i.e., for 2230 in thecase of FIGURE 4 with eight cylinders and pistons in each of thecylinder banks P P and P P4 FIGURE 4 exactly shows an upper half-sectionstaggered by 2230 in relation to the lower half-section. In each of thebores 13 cylindrical pistons such as 14 can slide radially thrusttowards the axis of the pump by a spring 15, bearing, on the outer side,on a hollow plug 16 fitted with a ball air cock 17. FIGURE 6 shows, asan alternative, a piston 18 provided with a swivel head 19.

Each radial bore or cylinder 13 of the bank P is connected with thecorresponding radial bore of the bank P by an aperture 20 drilled in thebody normal to said bores of cylinders. This also applies to the radialbores of the cylinder banks P and P All these drillings emerge in thesuction channel 9 and on this side are all fitted with suction valves21. On the opposite side, these drillings emerge in the delivery channel10 through a smaller diameter hole 22, which is provided with a deliveryvalve 23 at its end. Screw plugs 24 and 25 respectively afford access tothe suction and delivery valves.

The driving shaft 50 comprises a cylindrical part 26 for coupling withthe motor and a smaller diameter part 27 having longitudinal flutings.On this part of the shaft 4.- (FIGURE 5) four roller bearings areslipped whose internal rings 23 are eccentrically bored and machined inthis bore in the shape complementary to the flutings of the shaft 27. Bythis means these internal rings are keyed on to the shaft andcommunicate an eccentric movement to the external cages 29. The internalrings are successively fitted on in such manner that the eccentricitydirection is in opposition alternately at from each other. They are keptin position on the shaft by looking, on one side, between the shoulderdue to the difference in diameter of the parts 26 and 27 of the shaft,and on the other, a ring 39 secured by the screw 31 and small plate 32.

The shaft 50 is carried by two tapered roller bearings 33 and 34 mountedin opposition while forming plummetblocks. The bearing 33 is mounted inthe bore 7 of the body. The other bearing 34 is mounted in a side plate5 housed in the bore 4 of the body and comprising fixing members (screw36) for adjustment (screw 37) and fluidtightness (ring 38).

The shaft unit 50 and eccentric bearings together are so fitted that abearing is arranged in alignment with the pistons of each of thecylinder banks P P P and P4.

The machine thus made enables, in addition to the other advantagesafforded by the invention, an easy and speedy assembly and disassemblyof the control members formed by the shaft 50 and its bearings.

What I claim is:

1. In a machine having a plurality of cylinders and pistons reciprocabletherein, said cylinders being arranged in separate planes, each planehaving a plurality of cylinders arranged angularly disposed therein, theimprovement which comprises means for reciprocably actuating saidpistons and for balancing the reaction forces of said pistons, the lastmentioned means comprising a driven shaft rotatably mounted, said shafthaving a plurality of substantially linear, elongated, axially extendinggrooves disposed substantially parallel and angularly spaced in acircumferential direction thereon and terminating at one end of saidshaft, a plurality of removable bearings having outer peripheralsurfaces for reciprocably driving said pistons, said bearings having aninner bore having projections for complementary fitting into saidgrooves for rotatably driving said bearings with said shaft, saidbearings being mountable on said shaft over said end of said shaft andslipped off therefrom, disposed in operation axially on said shaft withone bearing in each of said planes, said planes being disposed axiallyalong said shaft, each passing through a respective bearing, saidcylinders being further arranged and said bearings having their boreseccentric each in a direction for displacing the pistons radially inalternate ones of said planes in opposite directions to cause thereaction forces of one of said planes to compensate by opposite reactionforces generated in a next adjacent plane.

2. In a machine having a plurality of cylinders and pistons reciprocablytherein, said cylinders being arranged in separate planes, each planehaving a plurality of cylinders arranged angularly disposed therein, theimprovement which comprises means for reciprocably actuating saidpistons and for balancing the reaction forces of said pistons, the lastmentioned means comprising a driven shaft rotatably mounted, said shafthavin a plurality of substantially linear, elongated, axially extendinggrooves disposed substantially parallel and angularly spaced in acircumferential direction thereon and terminating at one end of saidshaft, a plurality of removable bearings having outer peripheralsurfaces for reciprocably driving said pistons, said bearings having aninner bore having projections for complementary fitting into saidgrooves for rotatably driving said bearings with said shaft, saidbearings being mountable on said shaft over said end of said shaft andslipped off therefrom, disposed in operation axially on said shaft withone bearing in each of said planes, said planes being disposed axiallyalong said shaft, each passing through a respective bearing, said thepistons radially in one of two groups in opposite directions to causethe reaction forces of one of said groups of pistons to compensate byopposite reaction forces generated in the other of said groups ofpistons.

References Cited by the Examiner UNITED STATES PATENTS 1,216,378 2/17Thomas. 2,010,378 8/35 Sassen 10.3-174 2,050,578 8/36 Morreau 74-55 6Warner.

Huber 74-50 Orshansky 103-174 Whittingharn 103-174 Irving 74-55 Widmer74-49 Benedek 103-174 Navarro 103-174 Lane 103-174 Palmer 74-49BROUGHTON G. DURHAM, Primary Examiner.

DON A. WAITE, Examiner.

1. IN A MACHINE HAVING A PLURALITY OF CYLINDERS AND PISTONS RECIPROCABLETHEREIN, SAID CYLINDERS BEING ARRANGED IN SEPERATE PLANES, EACH PLANEHAVING A PLURALITY OF CYLINDERS ARRANGED ANGULARLY DISPOSED THEREIN, THEIMPROVEMENT WHICH COMPRISES MEANS FOR RECIPROCABLY ACTUATING SAIDPISTONS AND FOR BALANCING THE REACTION FORCES OF SAID PISTONS, THE LASTMENTIONED MEANS COMPRISING A DRIVEN SHAFT ROTATABLY MOUNTED, SAID SHAFTHAVING A PLURALITY OF SUBSTANTIALLY LINEAR, ELONGATED, AXIALLY EXTENDINGGROOVES DISPOSED SUBSTANTIALLY PARALLEL AND ANGULARLY SPACED IN ACIRCUMFERENTIAL DIRECTION THEREON AND TERMINATING AT ONE END OF SAIDSHAFT, A PLURALITY OF REMOVABLE BEARINGS HAVING OUTER PERIPHERALSURFACES FOR RECIPROCABLY DRIVING SAID PISTONS, SAID BEARINGS HAVING ANINNER BORE HAVING PROJECTIONS FOR COMPLEMENTARY FITTING INTO SAIDGROOVES FOR ROTATABLY DRIVING SAID BEARINGS WITH SAID SHAFT, SAIDBEARINGS BEING MOUNTABLE ON SAID SHAFT OVER SAID END OF SAID SHAFT ANDSLIPPED OFF THEREFROM, DISPOSED IN OPERATION AXIALLY ON SAID SHAFT WITHONE BEARING IN EACH OF SAID PLANES, SAID PLANES BEING DISPOSED AXIALLYALONG SAID SHAFT, EACH PASSING THROUGH A RESPECTIVE BEARING, SAIDCYLINDERS BEING FURTHER ARRANGED AND SAID BEARINGS HAVING THEIR BORESECCENTRIC EACH IN A DIRECTION FOR DISPLACING THE PISTONS RADIALLY INALTERNATE ONES OF SAID PLANES IN OPPOSITE DIRECTIONS TO CAUSE THEREACTION FORCES OF ONE OF SAID PLANES TO COMPENSATE BY OPPOSITE REACTIONFORCES GENERATED IN A NEXT ADJACENT PLANE.